TW201641907A - Selective oxy-fuel burner and method for a rotary furnace - Google Patents

Abstract

A selective oxy-fuel burner for mounting in a charge door of a rotary furnace, including at least two burner elements each oriented to fire into different portions of the furnace, each burner element including a selective distribution nozzle configured to flow a first reactant; and a proportional distribution nozzle configured to flow a second reactant; at least one sensor to detect one or more process parameters related to furnace operation; and a controller programmed to independently control the first reactant flow to each selective distribution nozzle based on the detected process parameters such that at least one burner element is active and at least one burner element is passive; wherein the second reactant is substantially proportionally distributed to the proportional distribution nozzles; and wherein the first reactant is one of a fuel and an oxidant and wherein the second reactant is the other of a fuel and an oxidant.

Description

Selective oxy-fuel burner and method for rotary kiln

The present invention is directed to a system for applying one or more oxy-fuel burners to a rotary kiln and a method for operating such a burner in a rotary kiln to provide enhanced heat transfer and energy efficiency.

As a result of the interaction between the refractory material and the metal bath as the furnace rotates, the melting efficiency of a conventional rotary kiln (e.g., remanufactured aluminum) is generally more efficient than a stationary furnace. In particular, the refractory material thermally transferred to the top of the metal bath can be converted into conduction and convection due to the rotation of the furnace and the refractory material becomes submerged under the metal bath. However, the flame-furnace interaction sometimes causes a heat or temperature striation or unevenness in the furnace, especially in a tilt rotary furnace, and especially in the furnace where unmelted debris interferes with the flame. The case of penetrating into the back side of the furnace.

In a conventional rotary kiln system, for example, in a two-way furnace (two-way furnace) as shown in Figs. 7, 8 and 9A to 9C, a nozzle mixing type (not premixed or diffused) burner 311 is installed in the furnace. The packing door (front end) 102 of 10 is generally ignited toward the center of the furnace head space 106 above the packing 104. With respect to this burner 311, combustion (the flame 312) is extended within the furnace 100 for a limited length, the furnace 100 defining a flame length, a flame structure, and an energy release profile. When the flame is fully deployed and unobstructed, as shown in Figure 7, the mixing and combustion of the fuel and oxidant will be complete. Due to the two-way design of the furnace, the flue gas duct 110 is typically located on or very close to the front end 102 of the burner 311. When the burner 311 is allowed to reach a fully deployed flame, the flame 312 extends to the vicinity of the opposite (back) end 103 of the furnace 100, and then the hot combustion gases 313 travel back to the flue gas duct 110, thereby obtaining a relatively long time. And exposing to transfer heat from the flame 312 to the filler 104 and the refractory material lining the furnace walls 108.

However, when the large chunks 105 of chips, ingots or scum are processed through the two-way rotary furnace 100, they often hinder the extension and deployment of the complete flame, as shown in FIG. When the flame 312 is obstructed, due to the short circulation of fuel and oxidant (incomplete combustion products 313) sent to the flue gas duct 110, it causes incomplete mixing in the furnace 100 and incomplete expansion of the flame. This in turn causes an increased flue gas temperature and energy loss of the furnace 100. It also causes uneven heating and/or melting of the filler material 104 in the furnace 100, which increases the likelihood of melt loss due to excessive heating of the front side portion 114 of the furnace 100 while leaving the back side 118 of the furnace 100 Cold spots and blockages (causing loss of productivity). In general, the firing rate of the burner 311 is erroneously increased when attempting to "arrival on the back side of the furnace 100", further exacerbating the problem.

Figures 9A through 9C show CFD modeling results for the case where the large ingot 105 or debris block hinders flame deployment. As shown in FIG. 9A, the flame 313 is offset from the front side surface of the large ingot 105, causing the hottest combustion gas to remain in the The front side of the ingot 105 and the front side portion 114 of the furnace 100 adjacent the burner 311 and the flue gas duct 310, while the intermediate portion 116 and the back side portion 118 of the furnace 100 receive less combustion product flow and less heat. Figure 9B shows that the front side surface of the ingot 105 that the flame 312 hits is very hot, while the back side of the ingot 105 and the melt are relatively cold. Figure 9C shows that the front side portion 114 of the furnace 100 is hot, perhaps overheated, while the back side portion 118 of the furnace 100 is still relatively cold.

The present invention provides a selective burner system and method for increasing the efficiency of filler melting in a rotary kiln and avoiding the possibility of overheating and oxidation of the filler. The burner configuration and operation method achieves optimal heat flux delivery in space and time, so that a more uniform temperature distribution can be achieved and maintained in the furnace, and a faster cycle time can be achieved. Uniform heat flux is achieved by directing the heat flux to the appropriate location, for example by algorithm, based on furnace process parameters and/or cycle time, or by one or more sensors. Based on feedback (real-time feedback), it is obtained after a certain period of time. The burner and method make it possible to encounter the filler in the furnace to provide improved melting while minimizing the loss of oxidative melt and making the selective longer and more penetrating flame possible. In particular, multiple high momentum flames are directed in a circular manner and surround the filler. Excessive heating is avoided and energy is more evenly distributed over the solid filler, furnace refractory, and the metal bath. The burner has a plurality of individual burner components located in a housing or dispersed in more than one housing. Each burner member has its own flame in a passive or active state, and the passive or active state can be adjusted according to different patterns and frequencies to achieve a desired heat flux distribution. shape. Each active flame is associated with a flame zone in the furnace.

Specifically, with regard to the rotary kiln, a sensor that is disposed at an appropriate position on the inside or outside of the furnace for detecting different process parameters associated with the furnace can be used to detect the presence of large unfused fragments and Heating streaks are developed, or the system can be programmed according to debris mixing (eg, if the fragments have large chunks or small chunks) to direct heat to one or more of the furnaces using multiple interrelated burner components position.

Different specific embodiments of the burner system will be described below.

Aspect 1. A selective oxy-fuel burner for a packed door mounted to a rotary kiln, the burner comprising: at least two burner components each igniting into a different portion of the furnace, each burner component comprising: a selectively distributed nozzle configured to flow out of the first reactant; and a proportional distribution nozzle configured to flow out of the second reactant; at least one sensor for detecting operation associated with the furnace One or more process parameters; and a controller programmed to independently control the first reactant flow to the respective selectively distributed nozzles based at least in part on the detected process parameters such that at least one burner The member is active and the at least one burner member is in a passive state, wherein a first reactant flow rate in the selectively distributed nozzle of the movable burner member is greater than an average first reactant flow rate to the selective distribution nozzle and the blunt The first reactant flow rate in the selectively distributed nozzle of the burner member is less than the average first reactant flow rate to the selective distribution nozzles; wherein the second reactant is Qualitatively distributed to the proportional distribution nozzles; and wherein the first reactant is one of a fuel and an oxidant and wherein the second reactant is the other of the fuel and the oxidant.

The burner of aspect 1, wherein one of the at least two burner members has a flame axis substantially perpendicular to the packing door and the other of the at least two burner members has the filler The vertical direction of the door sandwiches the non-zero angle, α, the axis of the flame; wherein the angle α is equal to or less than about 75°.

Aspect 3. The burner of aspect 1 or 2, wherein the at least one sensor comprises an overheating sensor for detecting overheating of the packing door, wherein at least one is being detected when excessive heating is detected The active burner member is converted to a passive state while at least one of the burner components remains unchanged or converted to activity.

Aspect 4. The burner of aspect 1 or 2, wherein the at least one sensor comprises an exhaust property sensor for detecting a change in one or more exhaust properties (eg, exhaust composition), wherein When the venting property indicates incomplete combustion, at least one of the active combustor components is converted to a passive state while at least one of the combustor components remains unchanged or transitions from a passive state to an active state.

Aspect 5. The burner of aspect 1 or 2, wherein the at least one sensor comprises an overheating sensor for detecting overheating of the packing door and for detecting one or more exhaust properties ( For example, a venting property sensor that varies in exhaust gas composition, wherein overheating is detected and the venting property indicates incomplete combustion, at least one active burner component is converted to a passive state, while at least one burner The component remains unchanged or transitions from passive to active.

The burner of any of aspects 1 to 5, wherein the at least one sensor comprises non-contact sensing for detecting the presence of a solid filler that would impede flame deployment in the furnace The solids are stored in the furnace and at least one of the active burner components is converted to a passive state while at least one of the burner components remains unchanged or transitions from a passive state to an active state.

The burner of any one of aspects 1 to 6, wherein the proportional distribution nozzle is annular in the burner member and surrounds the selective distribution nozzle.

A booster burner according to any one of aspects 1 to 7, further comprising: at least one segmented nozzle spaced apart from each of the burner members and configured to constitute an outflow assisted second reaction Wherein the controller is further programmed to control the staging ratio to be less than or equal to about 75%, wherein the segmentation ratio is a second reactant pair contained in the auxiliary second reactant flow The ratio of the total flow of the second reactant.

Aspect 9. A rotary furnace comprising: a packing door and an exhaust port disposed at one end of the furnace; and an oxy-fuel burner mounted to the packing door, the burner comprising: At least two burner members each igniting into different portions of the furnace, each burner member comprising: a selectively distributed nozzle configured to flow out of the first reactant; and a proportional distribution nozzle configured to An oxide can be flowed out; at least one sensor for detecting one or more process parameters in the furnace; and a controller programmed to independently generate the program independently based at least in part on the detected process parameters Controlling a first reactant flow to each of the selectively distributed nozzles such that at least one combustor member is active and at least one combustor member is passive, wherein the first reactant stream in the selectively distributed nozzle of the movable combustor member The amount is greater than the average first reactant flow rate to the selectively distributed nozzles and the first reactant flow rate in the selectively distributed nozzles of the passive burner member is less than that delivered to the selectively distributed nozzles Mean first reactant flow; wherein the second reactant is substantially proportionally distributed to the proportional distribution nozzle; and wherein the first reactant is fuel And one of the oxidants and wherein the second reactant is the other of the fuel and the oxidant.

Aspect 10. A method of operating a rotary kiln having a packing door and an exhaust port disposed at one end of the furnace and an oxy-fuel burner mounted to the packing door, the burner having a respective furnace toward the furnace At least two burner members igniting in different locations, each burner member comprising a selectively distributed nozzle and a proportional distribution nozzle, the burner additionally having a programmed program to independently control the selectively distributed nozzles delivered to each of the burner members a reactant flow wherein the second reactant flow rate to the proportional distribution nozzles is substantially proportionally distributed, the method comprising: flowing a second reactant through the annular nozzles at an oxidant flow rate; detecting one of the furnaces Or more process parameters; at least one of the burner components being at least partially active according to the detected process parameter selection and at least one of the burner components being passive; causing the first reaction Flowing through the selectively distributed nozzle of the at least one movable burner member at a reactive injection flow rate; flowing the first reactant through the at least one passive state at a passive injection flow rate a selectively distributing nozzle of the member; and causing the second reactant to flow substantially proportionally through the proportional distribution nozzles; wherein the active injection flow rate is greater than an average flow rate through the selectively distributed nozzles and the passive flow rate is less than An average flow rate of the selectively distributed nozzles; and one of the first reactant fuels and oxidants and wherein the second reactant is the other of the fuel and the oxidant.

Aspect 11. The method of aspect 10, further comprising: detecting excessive heating of the packed gate; and detecting excessive heating, converting at least one active burner member into a passive state while allowing At least one other burning The components remain active or converted to activity.

Aspect 12. The method of aspect 10 or 11, further comprising: detecting at least one exhaust property such as an exhaust composition; and converting at least one active combustor component when the exhaust property indicates incomplete combustion In a passive state, while at least one other burner component remains active or converted to activity.

The method of any one of aspects 10 to 12, further comprising: detecting when the at least one active burner member emits a flame that hits the solid filler in the furnace; and at least one of the foregoing The active burner member is converted to a passive state while at least one other burner member remains active or converted to activity.

The method of any one of aspects 10 to 13, wherein the ratio of the active injection flow rate to the passive injection flow rate is from about 5 to about 40.

The method of any one of aspects 10 to 14, wherein the passive burner member has an equivalence ratio of from about 0.2 to about 1, and wherein the movable burner member has an equivalence ratio of from about 1 to about 10, wherein The equivalence ratio is the ratio of the stoichiometric oxidant flow rate to the actual oxidant flow rate through the distributed nozzles to combust the fuel flowing through the remaining distributed nozzles.

Other aspects of the invention will be described below.

Α‧‧‧ burner member tilt angle

Β‧‧‧ burner member tilt angle

Γ‧‧‧ burner member tilt angle

A‧‧‧ burner components

B‧‧‧ burner components

C‧‧‧ burner components

D‧‧‧ burner components

A‧‧‧ activity jet

F1‧‧‧First fluid

F2‧‧‧Second fluid

F3‧‧‧ third fluid

P‧‧‧ Passive jet

Θ‧‧‧first angle

Θ‧‧‧second angle

10‧‧‧Selective booster burner

11‧‧‧Selective booster burner

12‧‧‧Ontology

14‧‧‧Face

20‧‧‧ burner components

20a‧‧‧ burner components

20b‧‧‧ burner components

20c‧‧‧ burner components

20d‧‧‧ burner components

22‧‧‧Selective distribution nozzle

23‧‧‧Control valve

24‧‧‧Circular proportional distribution nozzle

26‧‧‧Control valve

27‧‧‧ bypass passage

28‧‧‧Control valve

29‧‧‧Management

30‧‧‧section nozzle

32‧‧‧Control valve

100‧‧‧Rotary Furnace

102‧‧‧Filling door

103‧‧‧back side of the furnace

104‧‧‧Filling

105‧‧‧filling blocks

106‧‧‧Heating space

108‧‧‧ furnace wall

110‧‧‧ flue gas duct

112‧‧‧The flame of the active central burner component

112a‧‧‧ activity flame

112b‧‧‧ activity flame

112c‧‧‧ activity flame

112d‧‧‧ activity flame

113‧‧‧Incomplete combustion products

113a‧‧‧Combustion products

113b‧‧‧Combustion products

114‧‧‧ front part of the furnace

115‧‧‧Solid filler

118‧‧‧The back side of the furnace

120‧‧‧flame

122a‧‧‧flame

122b‧‧‧flame

124‧‧‧flame

134‧‧‧flame

150‧‧‧temperature sensor

152‧‧‧temperature sensor

153‧‧‧temperature sensor

154‧‧‧Temperature Sensor

155‧‧‧Exhaust property sensor

156‧‧‧ Optical Sensor

157‧‧‧Optical sensor

158‧‧‧ Near-end sensor

160‧‧‧temperature sensor

161‧‧‧pressure transducer

190‧‧‧ Controller

212a‧‧‧ activity flame

212b‧‧‧ activity flame

Figure 1A is an end perspective view of a particular embodiment of a selective burner with oxidant segments.

Figure 1B is a selective burner without oxidant segmentation. End perspective view.

Figure 2A is a schematic illustration of a specific embodiment of a selective burner having a segmentation as in Figure 1A.

Figure 2B is a schematic illustration of a specific embodiment of a selective burner without segmentation as in Figure 1B.

Figure 3 is a schematic illustration of the sequence of operations of the selective burner embodiment of Figures 1A and 1B.

Figure 4 is an end elevational view showing the nozzle orientation of two alternative burner embodiments.

Figures 5A(a) through 5A(e) are end views of different embodiments of a segmented selective burner. Figure 5A(a) shows the burner surrounded by four burner members whose central segmented nozzle is inclined radially outward; Figure 5A(b) shows the combustion of the central segmented nozzle surrounded by four burner members inclined along the circumscribed tangential line Figure 5A(c) shows a collinear arrangement of burners alternating the burner member with the segmented nozzles, wherein the central segmented nozzles are all outwardly inclined; Figure 5A(d) shows the segmented nozzles with long holes a burner of a quadrupole burner component adjacent to and substantially parallel to the spindle; and Figure 5A(e) shows a pair of aligned flat flame burner components adjacent to and substantially parallel to each burner member spindle and a pair of collinear Segmented nozzle.

Figures 5B(a) through 5B(f) are end views of different embodiments of a selective burner without segments. Figure 5B(a) shows a burner with four burner members tilted radially outward; Figure 5B(b) shows a burner with four burner members inclined along an circumscribed tangential line; Figure 5B(c) shows each with a different distance Burner of the collinear burner member inclined outwardly; FIG. 5B(d) shows a burner having a collinear burner member inclined outwardly from the adjacent pair and the other adjacent pair; and Figure 5B(e) shows a pair of straightening flat flame burner components. Figure 5B(f) shows a burner with multiple columns of collinear burner components.

Figures 5C(a) through 5C(d) are end views of other specific embodiments of a selective burner without segmentation. Fig. 5C(a) shows a burner having four burner members as shown in Fig. 16, in which there are three collinear burner members, one toward the axial direction of the burner and one inclined outward on either side, and the fourth burner member is inclined upward . Figure 5C(b) shows a burner having a trilinear combustor member, one toward the axial direction of the burner and one inclined outwardly on either side. Figure 5C(d) shows a burner having two burner components, an upper burner member in the axial direction of the burner and a lower burner member inclined downwardly toward the packing. Figure 5C(e) shows a burner having four components as shown in Figure 16 with a three-column burner member, a downwardly sloping central burner member, one inclined outwardly on either side, and the fourth burner member tilted upwardly. .

Figure 6 shows the different possible geometries of the distributed nozzles within each combustor component.

Figure 7 is a cross-sectional side view of a two-way rotary kiln having a conventional oxy-fuel burner mounted to the packing door and ignited in a conventional manner.

Figure 8 is a cross-sectional side view of a two-way rotary kiln having a large packing slab in the furnace of Figure 7, showing that the conventional flame that hits the large slab causes a short cycle of combustion products leaving the flu, which is thick Potential overheating and yield loss of the block, potential overheating of the front side of the furnace including the packed door, and insufficient heating of the back side of the furnace.

Figures 9A through 9C show graphs of computational fluid dynamics simulations of the furnace of Figure 8 with conventional flames hitting large packing chunks in the furnace. Figure 9A is the combustion temperature The degree profile shows that the highest combustion temperature is at the front of the slab where the flame is deflected and no substantial combustion products reach the back side of the furnace. Figure 9B is a temperature profile of the filler showing the high temperature on the front side of the slab where the flame is struck, the lower temperature on the back side of the slab, and the extremely low temperature in the molten packing on the back side of the furnace. Figure 9C is a temperature profile of the furnace wall showing the higher wall temperature of the front side of the furnace, the lower wall temperature of the back side of the furnace, and the steep temperature gradient across the bulk of the packing.

Figure 10 is a cross-sectional top plan view of a two-way rotary kiln of a selective burner embodiment mounted to the packed door showing the filler slab that the flame encounters in the furnace. The flame can be provided by a conventional burner or by a burner component of a selective burner.

Figure 11 is a cross-sectional top plan view of a two-way rotary kiln of a selective burner embodiment mounted to the packing door, showing the direction of the packing to avoid packing slabs in the furnace and creating a combustion product surrounding the packing. The stream is passed through the flame on the back side of the furnace. The selective burner has at least two burner components, one having a direct flame directed toward each side of the furnace.

Figure 12 is a cross-sectional top plan view of the dual-pass rotary kiln of the selective burner embodiment of the packing door of Figure 11, showing the burner member being movable to simultaneously direct the flame toward the sides of the furnace. Flow pattern.

Figure 13 is a cross-sectional top plan view of a two-way rotary kiln of a selective burner embodiment mounted to the packing door, showing the direction of the packing to avoid the packing slabs in the furnace and creating a combustion product surrounding the packing. The stream is passed through the flame on the back side of the furnace. The selective burner has at least four burner components with two different angles that direct the flame toward each side of the furnace.

Figure 14 is a cross-sectional top plan view of the dual-pass rotary kiln of the selective burner embodiment of the packing door of Figure 11, showing at least four burner members being movable to simultaneously direct the flame toward the sides of the furnace The flow pattern at different angles.

15A to 15C are graphs showing the results of computational fluid dynamics simulation of a furnace of a selective burner embodiment having a burner member as shown in Fig. 11, when the furnace has a large packing slab One side of the furnace is ignited; these figures can be directly compared to the results of Figures 9A through 9C for furnaces with conventional burners. Figure 15A is a graph of the combustion temperature profile, as compared to the conventional burner example of Figure 9A, which shows that the maximum combustion temperature is along the side of the chunk and extends further back to the furnace in the case of the selective burner. in. Figure 15B is a temperature profile of the filler, as compared to the conventional burner example of Figure 9B, which shows that there is no hot spot on the front of the chunk (because there is no flame touch) and The higher temperature of the molten filler is on the back side of the furnace. Figure 15C is a temperature profile of the furnace wall which, in the case of the selective burner, shows a more uniform wall temperature from the front side of the furnace to the back side as compared to the conventional burner example of Figure 9C.

Figure 16 is a cross-sectional end view of a two-pass furnace of a selective burner embodiment having four burner components, a combustor member arranged to direct the flame to a packing chunk in the furnace, the second combustor member being arranged The flame is directed around either side of the bulk of the packing in the furnace, and a burner member is arranged to direct the flame above the bulk of the packing in the furnace.

Figure 17 is a cross-sectional side view of a two-way rotary kiln of a selective burner mounted to the packing door, the burner having at least two burner configurations A piece comprising a burner member arranged to direct the flame downwardly toward the front side of the furnace and another burner member arranged to direct the flame toward the head space above the packing. The selective burner can be operated in three different modes: mode A is only pointing the flame toward the burner member in the headspace, mode B is only point to cause the flame to supply additional heat down the filler to melt in the furnace The front side portion still maintains the burner member of the solid packing, and mode C points the two burner members.

Figure 18 is a cross-sectional side view of a two-way rotary kiln of a selective burner embodiment mounted to the packing door, and showing different sensors that can be used alone or in combination to control the operation of the burner.

1A depicts a specific embodiment of a selective combustor 10 having a reactant segment (ie, a "segmented combustor"), while FIG. 1B depicts a selective boost combustor 11 without any reactant segmentation. An example (ie, no segmented burner). The burners 10 and 11 each include a body 12 having a face 14 wherein the burner 10 or 11 is mounted to a furnace (for example, as in Figure 7 or Figure 10) When in 15C or FIGS. 17-18), the face 14 is exposed to the combustion zone of the furnace.

The non-segmented combustor 11 includes a plurality of combustor members 20 (see FIG. 4) that are oriented to define an circumscribed circle, and the combustor members 20 are preferably equally spaced around the circumscribed circle. The segmented burner 10 additionally includes at least one segmented nozzle 30 disposed in position within the circumscribed circle. For the purpose of reference, a moving jet (A) and a passive jet (P) are depicted to show that the active jet has a larger flame than the passive jet.

The burners 10 and 11 respectively depicted in Figures 1A and 1B each have four burner members 20 spaced apart at approximately 90° intervals. However, it is understood that the burner 10 or 11 may include any number n of burner members 20 equal to or greater than two. For example, the combustor 10 or 11 may have two burner members 20 that are spaced apart diametrically opposite (as shown in Figures 5A(d) and 5B(d)), or alternatively spaced about 120° apart. The open three burner members 20, or five or more burner members 20 spaced apart by odd numbers. It is also known that with regard to furnace geometry, configuration or operating conditions, it may be desirable to have a burner 10 or 11 having a plurality of burner members 20 non-equally spaced around the circumscribed circle. In another alternative, the burner 10 or 11 may have a geometry other than a circle defined by the geometry and configuration of the furnace, for example elliptical or irregular polygons, many of the burner components 20.

In addition, the non-segmented burner 11 can include multiple housings placed in different locations at different locations in the furnace, but two or more burner components 20 operating in a synergistically selective manner as described herein, rather than All burner members 20 in the same housing.

The segmented burner 10 of Figure 1A has a segmented nozzle 30 disposed centrally. However, salty knowledge may be equipped with a plurality of segmented nozzles 30, wherein the segmented nozzles 30 may all be the same size or different sizes. Incidentally, depending on the furnace geometry, the desired flame characteristics, the orientation of the individual burner components 20, and other factors, the (equal) segmented nozzles 30 may be eccentrically disposed within the circumscribed circle defined by the burner members 20. The segmented nozzle 30 can be of any shape.

In both the segmented combustor 10 and the non-segmented combustor 11, each combustor member 20 includes an option surrounded by an annular proportional distribution nozzle 24. The nozzle 22 is selectively distributed. A selectively distributed reactant flows through the selective distribution nozzle 22, and a proportional distribution reactant flows through the annular proportional distribution nozzle 24, one of which is a reactant fuel and the other is an oxidant. In the segmented burner 10, a portion of the proportional distribution reactant also flows through the segmented nozzle 30. In one embodiment of the combustor 10 or 11, a fuel system flows through the selectively distributed nozzle 22 as the selectively distributed reactant, and an oxidant stream flows through the annular proportional distribution nozzle 24 as the proportional distribution reactant. In another embodiment of the combustor 10 or 11, the oxidant flows through the selectively distributed reactants of the selectively distributed nozzles 22 and the fuel system flows through the proportions of the annular proportional distribution nozzles 24 to distribute the reactants. Moreover, in an alternative embodiment of the burner member 20, the proportional distribution nozzle 24 is not necessarily annular, but can include one of the appropriate locations disposed in close proximity to the selective distribution nozzle 22 or More nozzles. For example, a proportional distribution nozzle 24 may be adjacent to the selective distribution nozzle 22, or a plurality of proportional distribution nozzles 24 may be disposed adjacent to or circumferentially around the selective distribution nozzle 22. In any configuration, the proportional distribution nozzle 24 (or nozzle 24) is supposed to be close enough to the selective distribution nozzle 22 to cause the fuel and oxidant to interact with each other and to burn to form a stable flame.

In the segmented burner 10, the ratio of the proportional distribution reactants introduced through the annular proportional distribution nozzles 24 can be adjusted to maintain stable burner operation and/or control flame properties, for example, as compared to the segmented nozzles 30. Heat release curve. The phrase "segment ratio" means the amount of proportional distribution reactant flowing through the segment nozzle 30 divided by the total amount of reactants flowing through the segment nozzle 30 and the proportional distribution nozzles 24 of the annular proportional distribution nozzles 24.

As used herein, the phrase "fuel" means any hydrocarbon-containing material that can be used as a fuel in a combustion reaction. Preferably, the fuel is a gaseous fuel, such as natural gas, but the fuel may also be an atomized liquid fuel or a pulverized solid fuel in the carrier gas. As used herein, the phrase "oxidant" means any oxygenate that is capable of oxidizing a fuel in a combustion reaction. The oxidant may be air, dirty air (i.e., a gas containing less than about 20.9% oxygen), oxygen-enriched air (i.e., a gas containing more than about 20.9% oxygen) or substantially pure oxygen (i.e., containing About 100% oxygen gas). In various embodiments, the oxidant is oxygen-enriched air having an oxygen concentration of at least about 23%, at least about 26%, at least about 40%, at least about 70%, or at least about 98%.

The selective distribution nozzle 22 may have any shape. A subset of possible exemplary shapes is shown in Figure 6, which includes a long hole nozzle (Figure 6a), a single long hole nozzle (Figure 6b), a circular nozzle (Figure 6c), and a multi-hole nozzle (Figure 6d). A more detailed discussion of a possible nozzle shape can be found in US 6,866, 503, which is incorporated herein in its entirety by reference. For example, in order to generate a luminescent flame by high radiation transfer properties, a selective distribution nozzle 22 having a shape factor of less than 10 can be used, and in order to produce a non-luminescent flame that may have a lower NOx, a shape factor of 10 or greater can be used. The selective distribution of nozzles. The illumination mode may be preferred in terms of melting operation. Note that high form factor nozzles can include porous nozzles. As described in detail in US 6,866,503, the form factor, σ, is defined as the perimeter, the square of P, divided by the double cross-sectional area, A, or defined by the equation: σ = P ² /2A.

As shown above, FIG. 2A shows a simplified control diagram of the segmented burner 10, and FIG. 2B shows a simplified control of the non-segmented burner 11. intention. The first fluid F1 is supplied to the selective distribution nozzles 22 at a total flow rate controlled by the control valve 23. The flow rate of the first fluid F1 to each of the selective distribution nozzles 22 is separately controlled. In one embodiment, the control valve 26 upstream of each of the selectively distributed nozzles 22 is adjusted between a high flow rate and a low flow position, respectively corresponding to the active state of the burner member 20 containing the selective distribution nozzle 22 and blunt State. In an alternative embodiment, the control valve 26 is arranged in parallel with the bypass passage 27. In this embodiment, the control valve 26 is adjusted between the open position and the closed position, and further corresponds to the active and passive state of the burner member 20, respectively, and the bypass passage 27 allows for a smaller amount of flow. The control valve 26 can be bypassed, so that some of the first fluid F1 always flows to the selective distribution nozzle 22, even in the passive state. The flow rate to each of the selective distribution nozzles 22 can be adjusted such that the flow rate of the active state of the first fluid F1 sent to each of the selective distribution nozzles 22 may be different or the same, and the first fluid supplied to each of the selective distribution nozzles 22 The flow rate of the passive state of F1 may be different or the same depending on the requirements of the particular furnace or application.

The effect of either configuration is to adjust the flow through the selective distribution nozzle 22 between a relatively high active flow rate and a relatively low passive flow rate. For example, the active flow rate can be defined as a flow rate greater than the average flow rate delivered to the selectively distributed nozzles 22, while the passive flow rate can be defined as a flow rate less than the average flow rate delivered to the selectively distributed nozzles 22. The average flow rate is obtained by dividing the total flow rate of the first fluid F1 by the total number n of the selective distribution nozzles 22/burner members 20. Other relationships between the active flow rate and the passive flow rate can be used, and the active flow rate is always greater than the passive flow rate.

Regardless of the activity and the passive flow rate, the passivation flow rate must Must be greater than 0 flow. The passive flow rate is sufficient to maintain combustion in each combustor member 20 to provide a mechanism for immediate ignition when the combustor member 20 transitions from the passive state to the active state. This non-zero passive flow rate also prevents foreign matter from entering the selective distribution nozzle 22. In a specific embodiment, the passive flow rate is less than or equal to one half of the active flow rate. In another embodiment, the ratio of the active flow rate to the passive flow rate is at least about 5 and no greater than about 40. In yet another embodiment, the ratio of the active flow rate to the passive flow rate is at least about 15 and no greater than about 25.

The second fluid F2 is supplied to the annular proportional distribution nozzles 24. The control valve 28 controls the total flow rate of the second fluid F2 to the annular proportional distribution nozzles 24, and the manifold 29 distributes approximately equal to the flow rate across the n annular proportional distribution nozzles 24.

In the segmented burner 10 (Fig. 2A), rather than in the non-segmented burner 11 (Fig. 2b), a third fluid F3 is supplied to the segmented nozzle 30, and the flow rate of the third fluid F3 It is controlled by the control valve 32. The segmented nozzle 30 can include scrolling vanes or other mechanisms (not shown) that are vortexed by the third fluid F3 that exits the segmented nozzles 30. The vortex applied to the third fluid F3 will cause the fluid jet to collapse, which can assist the third fluid F3 jet to be atomized by the (e) active jet. However, strong vortexing is not desirable because it may dominate the flow structure and change the shape of the flame.

The second fluid F2 and the third fluid F3 contain any of the same type of reactants, fuels or oxides. For example, when the first fluid F1 is a fuel, the second fluid F2 and the third fluid F3 are each an oxidant, and when the first fluid F1 is an oxidant, the second fluid F2 and the The third fluid F3 is each a fuel. In a specific embodiment, the second fluid F2 and the third fluid F3 are different fluids, that is, each have the same reactant (fuel or oxidant) but different concentrations. In this case, the control valve 28 and the control valve 32 must be separate valves to control the two fluids F2 and F3. In an alternative embodiment (not shown), the segment valve can replace the control valve 28 when the second fluid F2 and the third fluid F3 are the same fluid of the same concentration of the same reactant. The control valve 32 is configured to distribute a portion of the flow of the n proportional distribution annular nozzles 24 and the remainder of the flow to the segmented nozzles 30.

In the particular embodiment depicted in Figures 2A and 2B, the flow rate of the second fluid F2 to each of the annular proportional distribution nozzles 24 is not separately controlled. As a result, each of the annular proportional distribution nozzles 24 always flows out of the average flow rate of the second fluid F2 when the control valve 28 is opened. The average flow rate is obtained by dividing the total flow rate of the second fluid F2 by the total number n of the annular proportional distribution nozzles 24/burner members 20. Alternatively, the flow rate of the second fluid F2 sent to each of the annular proportional distribution nozzles 24 can be individually controlled.

In the particular embodiment depicted in Figures 2A and 2B, because the flow rate of the second fluid F2 delivered to each of the annular proportional distribution nozzles 24 is about the same, each burner member 20 is then active or blunt depending on whether the burner member 20 is at the time. The state is based on one of the two sides of the metering chemical operation. When the burner member 20 is in the active state, the burner member 20 is disengaged from metering chemistry, and sometimes completely disengages from metering chemistry, operating in one direction, and when the burner member 20 is in the passive state, The burner member 20 is out of metering chemistry and sometimes completely disengages from the metering chemistry and operates in the opposite direction. for example, When the first fluid F1 is a fuel and the second fluid F2 is an oxidant, the combustor member 20 in the active state can operate in a fuel-rich manner and the combustor member 20 in the passive state can be fuel-poor Mode operation. Alternatively, when the first fluid F1 is an oxidant and the second fluid F2 is a fuel, the burner member 20 in the active state can operate in a fuel-poor manner and the burner member 20 in the passive state can be rich The way the fuel operates. However, since the total flow of fuel and oxidant is controlled by control valves 23 and 28 (and also by segment control valve 32), no matter how many burner members 20 are in the active state and the passive state In contrast, the overall metering chemistry of the burner 10 is still the same.

The metrological chemistry of each burner member 20 in operation can be characterized by an equivalence ratio. With respect to the specified fuel flow rate, the equivalent ratio is calculated as the ratio of the stoichiometric chemical oxygen flow to the actual oxygen flow. Regarding the oxidant which is 100% oxygen, the oxygen flow rate is equal to the oxidant flow rate. With respect to the oxidant having an oxygen percentage X of less than 100%, the oxygen flow rate in the oxidant stream is determined by dividing the oxidant flow rate by the oxygen percentage X; for example, in order to satisfy the oxygen requirement of 100 SCFH using an oxidant containing 40% oxygen , requires 250 SCFH of oxidant.

The following discussion relates to the first fluid F1 fuel and the second fluid F2 oxidant (non-segmented burner), and the first fluid F1 fuel and the second fluid F2 and the third fluid F3 are both A specific embodiment of an oxidant (segmented burner). When the burner member 20 is in the passive state, the equivalent ratio is less than about 1, and preferably at least about 0.2. This means that the passive burner component 20 utilizes up to five times the oxygen operation required for complete combustion in a fuel-poor manner. In contrast, when the burner member 20 is in the active state, the The equivalent ratio is greater than about 1, and preferably no greater than about 10. This means that the active burner member 20 operates in a fuel-rich manner with less than 10% of the oxygen required for complete combustion.

The segmentation ratio, in the case of a segmented burner, is defined as the ratio of the amount of reactant flowing through the segmented nozzle 30 to the total amount of reactants flowing through the annular proportional distribution nozzles 24 and the segmented nozzles 30. For example, when the second fluid F2 and the third fluid F3 are oxidants, the segment ratio is the amount of oxygen supplied by the segment nozzle 30 divided by the segment nozzle 30 and the annular proportional distribution nozzles 24 . The total amount of oxygen supplied together. If the second fluid F2 and the third fluid F3 are the same fluid (ie, have the same oxygen concentration), the segment ratio is simply the flow rate of the third fluid F3 divided by the flow rate of the second fluid F2 and The sum of the flow rates of the third fluid F3. However, if the second fluid F2 and the third fluid F3 are different fluids (that is, have different oxygen concentrations X2 and X3, respectively), the segmentation is calculated as X ₃ F ₃ /( X ) taking the concentration difference into consideration. ₂ F ₂ + X ₃ F ₃ ), as is known to those skilled in the art.

The segmented burner 10 is preferably operated by a segmentation ratio equal to or less than about 75%. For example, when the oxidant is segmented, that is, when the second fluid F2 and the third fluid F3 are oxidant, at least about 25% of the oxygen sent to the combustor 10 flows through the annular proportional distribution. Nozzle 24 also causes no more than about 75% of the oxygen to flow through the segmented nozzle 30. More preferably, the segmented burner 10 is operated by a segmentation ratio equal to or less than about 40%. Still further, as discussed above, due to the active or passive operation of each of the burner members 20, the first fluid F1 that utilizes a stoichiometric excess is utilized for one or more combustor members 20 that are active at a time. Operation, while passive one or more burner components 20 The operation is performed with a second fluid F2 that is more than a stoichiometric excess, thereby providing some micro-segmenting effects, even without taking into account the third fluid F3 provided by the segmented nozzles 30.

Moreover, even the non-segmented burner 11 is operated by a slight "segmentation" effect, wherein the movable burner members 20 operate in a manner rich in the first fluid F1 and the passive burner components are The first fluid F1 operates in a lean manner such that some of the first fluid F1 from the active combustor members 20 is combusted in a more delayed manner by some of the second fluid F2 from the passive combustor members 20 . For example, when the first fluid F1 is a fuel and the second fluid F2 is an oxidant, the movable combustor members 20 are rich in fuel, and the excess fuel somewhat utilizes an excess of the passive burner member 20 from fuel lean. The oxidant burns.

The first fluid F1 of the leaving activity selective distribution nozzle 22 has a movable jet velocity that depends on the flow rate of the first fluid F1 and the cross-sectional area of the selective distribution nozzle 22. The second fluid F2 leaving the annular proportional distribution nozzle 24 has an annular jet velocity that depends on the flow rate of the first fluid F2 and the cross-sectional area of the annular proportional distribution nozzle 24. In the segmented burner 10, the third fluid F3 leaving the segmented nozzle 30 has a segmented jet velocity that depends on the flow rate of the third fluid F3 and the cross-sectional area of the segmented nozzle 30. The active jet velocity is preferably higher than the annular jet velocity for both the segmented burner 10 and the non-segmented burner 11.

In addition, for optimum performance of the segmented burner 10, the segmented jet velocity should be less than or equal to the active jet velocity and greater than or equal to about 0.05 times the active jet velocity. In a specific embodiment, the The ratio of the segmented jet velocity to the active jet velocity is less than or equal to about 0.4. In another embodiment, the ratio of the segmented jet velocity to the active jet velocity is greater than or equal to about 0.1.

In an exemplary embodiment of a vertical ignition device (mounted on the top), the first fluid F1 jet velocity through the active selective distribution nozzle 22 is at least about 250 ft/s and preferably at least about 300 ft/s. Moreover, the velocity through the passively selectively distributed nozzle 22 is about 20% of the active jet velocity. With regard to a horizontal ignition device, the active jet velocity may be quite low because less effort is required to remove the floating effect to avoid overheating of the burner block.

All control valves 23, 26, 28 and 32 are connected to and controlled by controller 105, which is clearly programmed or constructed to operate the combustor 10. The controller 105 can include conventional electronic device components such as CPU, RAM, ROM, I/O devices, and the programming or configuration of the controller 105 can be by hardware, firmware, software, and now known or later developed. A combination of one or more of the other means for writing the operational instructions to the controller is completed.

As noted above, one of the fluids F1 and F2 must or contain fuel, and the other of the fluids F1 and F2 must be an oxidant or contain oxygen. In a segmented burner 10, the third fluid F3 should be the same type of fluid (fuel or oxidant) as the second fluid F2. The fuel may be a gaseous fuel, a liquid fuel or a pulverized solid fuel in a gaseous carrier. In one embodiment of the non-segmented burner 11, the F1 is a fuel and the F2 is an oxidant. In one embodiment of the segmented burner 10, the F1 is fueled and F2 And F3 oxidant. In this case, F2 and F3 may be the same oxidant, or F2 and F3 may be different oxidants. For example, in a preferred embodiment, for a segmented combustor 10 or a non-segmented combustor 11, F1 is a gaseous fuel such as natural gas, and the F2 is an oxidant having an oxygen concentration equal to or greater than about 70%. For the segmented burner 10 in this embodiment, the F3 concentration is equal to or greater than about 20.9% of the oxidant. In another similar embodiment, the F1 is a gaseous fuel such as natural gas, the F2 is an oxidant having a greater oxygen concentration than the air, and in the segmented burner version, the F3 is air.

In an alternative embodiment, the F1 is an oxidant and the F2 (and F3 in the segmentation case) is a fuel. In this case, the oxygen concentration of F1 is equal to or greater than about 26%, preferably equal to or greater than about 40%, and more preferably equal to or greater than about 70%.

Figure 3 shows a possible operational sequence for one of the specific embodiments of the burners 10 and 11 illustrated in Figures 1A and 1B. For purposes of discussion, the four burner components 20 are labeled a, b, c, and d. As shown, only one combustor member 20 is active at a time, while the remaining combustor member 20 is passive, and each combustor member 20 is successively converted into a transition when the previously active combustor member 20 returns to the passive state. The status of the event.

In particular, in the particular embodiment depicted, the burner member 20a is active while the burner members 20b, 20c, and 20d are passive. In other words, each of the annular nozzles 24 in each of the combustor members 20 is receiving a second fluid F2 of approximately equal flow, and only the selectively distributed nozzles 22 in the combustor member 20a are receiving a first fluid F1 of higher activity. , while the selective distribution nozzles 22 of the other burner members 20b, 20c, and 20d are receiving a lower blunt The flow rate of the first fluid F1. This causes a longer and more penetrating flame from the movable burner member 20a and a shorter (ignition) flame from the passive burner members 20b, 20c and 20d. As further depicted by the depicted embodiment, when the combustor member 20b becomes active, the combustor member 20a resumes the passive state and the combustor members 20c and 20d remain passive. Next, when the burner member 20c becomes active, the burner member 20b returns to the passive state and the burner members 20c and 20a remain passive. Finally, when the burner member 20d becomes active, the burner member 20d returns to the passive state and the burner members 20a and 20b remain passive.

The sequence shown in Figure 3 and described above is only one of substantially unrestricted variations. In a non-limiting example, a burner member 20 is active at a time in a repeating sequence such as a-b-c-d or a-b-d-c or a-c-b-d or a-c-d-b. In another non-limiting example, a burner component 20 is in a random sequence at a time. In yet another non-limiting example, a burner component 20 is active at a certain time, but each time passes the same or a different length of time.

Again, in other examples, more than one combustor member 20 is active at a certain time. For example, with respect to the combustor 10 having three or more combustor components 20, the two combustor components 20 can be active and the remainder are passive. In general, with respect to the burners 10 having n burner members, any number of burner members 1 through n-1 may be active and the remainder being passive.

Each of the burner members 20 can be converted from the passive state to the active state in accordance with a predetermined algorithm according to a predetermined algorithm according to a predetermined algorithm, in accordance with furnace conditions or in synchronization with other cycles or periodic events of the furnace. One or more Multiple sensors 195 may be placed in the proper location of the furnace for sensing any parameters that may be relevant to determining how much heat of combustion is needed there. For example, the sensor may be a temperature sensor such that when the temperature sensor is below a threshold setting, the burner member 20 adapted to heat the temperature sensor region of the furnace may be further Become active on a frequent or longer period. Or if the temperature sensor detects that a portion of the furnace or packing receives insufficient heat, then one or more of the burner members 20 are placed at appropriate locations near the furnace portion or tilted toward the portion of the packing. In the active state, the burner member 20 in the furnace portion that has received excessive heat is converted to the passive state. Specifically speaking, with regard to a regenerator, a temperature sensor, such as an optical sensor, can detect the temperature of the filler in different parts of the furnace and detect areas that require additional heat, such as all or part of the cold spot 122, and target those The burner members 20 of the region can become active for a longer period of time or more frequently to increase the temperature of those regions.

The temperature sensor may include a contact sensor such as a thermocouple or RTD located in the furnace wall, or a non-contact sensor such as an infrared sensor, a radiation sensor, an optical sensor, a camera, a sense of color Other sensors available in the detector or in the industry. Other types of sensors can also be used to indicate the degree of melting or heating in the furnace, including but not limited to a proximal sensor (eg, sensing proximity to a molten solid filler) or a conductivity sensor (For example, detecting a higher conductivity of a liquid compared to a solid slab that is not interconnected).

Several benefits can be achieved by operation of the combustor 10 or combustor 11 as described herein. Because the thermal energy is preferentially aligned to a certain location and over a longer or shorter period of time, the cold spots in the furnace can be resolved and removed, resulting in more uniform heating and melting. Especially for the vertical ignition device of Figure 7 or Figure 15. Arranging (ie, mounted on the top-down burner), operating the burner in an active mode with less than all of the burner components 20 reduces or eliminates the hazard of the floating flame, thereby avoiding the burner brick and the roof Overheated. The fuel-rich combustion caused by the movable burner member 20, in the case where the oxygen supplied through the annular proportional distribution nozzle 24 is significantly less than the metered chemical oxygen required for the fuel supplied through the selective distribution nozzle 22, in the melting A non-oxidizing atmosphere is created near the bath to help prevent improper oxidation of the filler. Incidentally, the activation of the burner members 20 in the repetitive cycle mode can be used to generate a vortex heating mode that increases the residence time of the combustion gases, increases the rate of heat transfer, and improves heating uniformity, such as, for example, US 2013/ Shown in 00954437. Further, the burner member 20 is selectively activated and the section ratio is varied to adjust the position of the maximum heat flux radiated by the combustion reactions and to adjust the flame coverage in accordance with different furnace geometries, conditions, and fill levels.

Different possible configurations of the segmented burner 10 and the non-segmented burner 11 include those shown in Figures 5A and 5B. In a particular embodiment of the type shown in Figures 5A(a) and 5B(a), one or more of the burner members 20 may be circumscribed from the burner member 20 or from the burner brick The axis of the 12 or the axis defined by the segmented nozzle 30 is inclined radially outward by an angle a. Although the depicted embodiment shows that all of the four combustor members 20 are inclined radially outwardly by the same angle a, it is understood that each combustor member 20 may be tilted at different angles depending on the furnace geometry and the desired operational characteristics of the combustor 10. . The angle α may be equal to or greater than about 0° and preferably non-zero and equal to or less than about 75° (or conversely, the complementary angle measured from the plane of the burner face 14 is about 15° to about or slightly lower At 90°). Preferably, the angle α is equal to or less than about 60°. More preferably, The angle a is at least about 10 and no greater than about 40.

In the particular embodiment of the type illustrated in Figures 5A(a) and 5B(a), one or more of the combustor members 20 may be inclined at an angle β to the circumscribed circle to create a vortex. Although the depicted embodiment shows that all of the four burner members 20 are inclined at the same angle β along a tangential line, it is understood that each of the burner members 20 may be inclined at different angles β _n depending on the furnace geometry and the desired operational characteristics of the burner 10. . The angle β may be equal to or greater than about 0° and preferably equal to or less than about 60°. More preferably, the angle β is at least about 10° and no greater than about 40°.

In the particular embodiment of the type shown in Figures 5A(c) and 5B(d), most of the combustor members 20 are arranged substantially collinearly with each other to define a line having a center point and an end. Although four burner components 20 are shown, this embodiment is suitable for having at least two burner components 20 (for example, as shown in Figure 5B(c) for a non-segmented burner) up to a particular furnace. As many configurations as possible of the burner member 20 are required. In a segmented burner, the segmented nozzles 30 are disposed at appropriate locations between adjacent pairs of burner members 20 such that the burner members 20 and the segmented nozzles 30 are arranged in turn. For example, a device having two burner members 20 places a segmented nozzle 30 in position between the two burner members 20, and a device having three burner members 20 places the two segment nozzles 30 in A suitable position between a pair of adjacent burner members 20. The burner members 20 may all be perpendicular to the burner face 14, or some or all of the burner members 20 may be inclined outwardly from the line center point toward one of the line ends by less than or equal to about 45°. The angle γ. Likewise, the segmented nozzles 30 may be perpendicular to the burner face 14, or some or all of the segmented nozzles 30 may be along one or the other along the line. Specific embodiments depicted The central segmented nozzle 30 is perpendicular to the burner face 14 and has a set of trilinear member-burner members 20, segmented nozzles 30, and another combustor member 20 disposed on either side of the diameter, and From the central segmented nozzle 30 outward and towards the individual ends of the line.

In the particular embodiment of the type shown in Figures 5A(d) and 5B(d), most of the combustor members 20 are arranged in line with each other to define a line having a center point and an end. Although four burner components 20 are shown, this configuration is suitable for configurations having at least two burner components 20 up to as many burner components 20 as may be required in a particular furnace. In a segmented burner, an elongate or substantially rectangular segmented nozzle 30 having at least 1.5 times the major axis of the minor axis is disposed adjacent to and spaced from the burner member 20 The distance is fixed and the spindle is substantially parallel to the line defined by the burner members 20. The burner members 20 may all be perpendicular to the burner face 14, or some or all of the burner members 20 may be inclined outwardly from the line center point toward one of the line ends by less than or equal to about 45°. The angle γ.

In the specific embodiment of the type shown in Figures 5A(e) and 5B(e), each burner member 20 has a flat flame configuration wherein both the selective distribution nozzle 22 and the annular nozzle 24 have a short major axis. The shaft is at least 1.5 times longer or larger than the rectangular configuration. This type of flat flame burner is described in more detail, for example, in US 5,611,682. In the segmented burner, at least two segmented nozzles 30 are disposed adjacent to and spaced apart from the burner members 20 and are generally collinearly oriented to define the burner The main axes of the members 20 are substantially parallel lines. At least two burner members 20 are utilized in this configuration.

In any of the above-described configurations of Figures 5A and 5B, the selective operation scheme can be implemented in a similar manner to the configuration of Figures 1A and 1B above. In particular, at least one burner component 20 operates in an active state at any particular time, wherein the fluid flow through the active selective distribution nozzle 22 is greater than the average fluid flow through all of the selective distribution nozzles 22, and at least one burner The 20 series is in a passive state in which the fluid flow through the passive selective distribution nozzle 22 is less than the average fluid flow through all of the selective distribution nozzles 22.

Figures 10, 11A, 11B, 12, 13 and 14 show different modes of operation that can be achieved with the burner 11, for example as shown in Figure 5C(a), Figure 5C(b) or Figure 5C(c), the combustion The vessel 11 has a central burner member 20 that is axially oriented along the burner 11 (i.e., substantially perpendicular to the burner face 14), and at least one pair of symmetric side combustor members 20, one of which has a combustion The member 20 is disposed at a suitable position on either side of the central burner member 20 from the side and is inclined outward. In a particular embodiment, such as FIG. 5C(c), the inner pair of inclined combustor members 20 that are closer to the central combustor member 20 can be angled to the combustor member 20 as compared to the outer side that is further from the central combustor member 20. Tilt outwards at a smaller angle. Similarly, the mode of operation shown in Figures 11 and 12 can utilize a burner as shown in Figures 5B(c), (d), 5B(e), 5B(f), 5C(b) or 5C(c). 11 is achieved, and the operation modes shown in Figs. 11, 12, 13 and 14 can be achieved by the burner 11 as shown in Fig. 5B(d), 5B(f) or 5C(c). For example, when measured from the axial direction of the burner, the inner pair can be inclined outwardly by a first angle α of about 10° to about 45°, and preferably about 15° to about 30°, and the outer pair can be oriented The outer angle is inclined by a second angle of from about 15° to about 75°, and preferably from about 30° to about 60°.

In addition to this, most of the burner components can be inclined downward toward the packing at different angles. The central burner member 20 can be substantially parallel (or substantially perpendicular to the burner face 14) to the burner axis, and the inner pair of inclined burner members 20 can be inclined downwardly from about 0° to about 60°. An angle θ and the outer pair of inclined burner members 20 can be inclined downward by a second angle θ of from about 0° to about 60°. In one embodiment, the inner pair of inclined combustor members 20 are angled downwardly by about 30 to about 60 to enable heating of the solid filler remaining adjacent the packing door of the furnace while the outer pair is facing the burner member 20. Tilting downward from about 10° to about 45° hits the surface of the packing along the wall of the furnace.

In the first mode of operation (mode 1) of Figure 10, only the central combustor member 20 is active while the multi-tilt combustor member 20 is in a passive state. This mode is the same as the prior art mode of Figure 7, and produces a single flame 112. If the furnace 100 has a large packing slab 105 (or multiple relatively large solid packing blocks) in the center, as shown, the flame 112 of the movable central burner member 20 will hit the slab 105 and take the least resistance path. And the fuel and oxidant (incomplete combustion products) 113 circulate briefly away from the flue gas duct 110. This results in an uneven heat distribution in the furnace 100 wherein the front side portion 114 of the furnace 100 is overheated, the flue gas temperature is increased, and the back side portion 118 of the furnace 100 is cold. Although the thermal conversion rate of the flame 112 to the ingot 105 is high due to direct contact, this may cause problems such as excessive heating and oxidation. The potential overheating due to the packing in the center of the furnace 100 and the problem can be measured by the mode 1 operation by measuring the temperature of the packing door 102, the temperature of the flue gas duct 110, and the temperature of the back side portion 118 of the furnace 100. And/or one or more exhaust properties, such as the exhaust gas composition of the flue gas, to detect Measurement. Thus, although this mode of operation may be beneficial for a short period of time by causing the flame to hit the solid filler, it is desirable for the packing door 102 and/or the flue gas duct 110 to show signs of overheating and/or the back of the furnace 100. The temperature of the side portion 118 indicates an indication of insufficient heating to convert the central combustor member 20 to a passive state and to convert one or more other combustor members 20 into activity.

In the second mode of operation (mode 2A or mode 2A) of Figures 11A and 11B, the central burner member 20 is made passive while one of the inclined burner members 20 is active to create a slanted flame 112a. . In one embodiment, in the combustor 11 of FIG. 5C(b), as exemplified, a combustor member 20 is active and the two combustor members 20 are passive. Alternatively, in another embodiment, in the combustor 11 of Figure 5C(c), a combustor member 20 is active and the four combustor member 20 is passive. Other exemplary burners 11 can be used to create the same flame type. Note that in this mode, the central combustor member 20 can also cycle between active and passive states while maintaining the remaining combustor members 20 in their same state. This mode of operation causes the active flames 112a, 112b to bypass the solid packing 105 in the center of the furnace 110 so that thermal energy reaches the back side portion 118 of the furnace 110. As shown in Figures 11A and 11B, the circulation of the products of combustion 113a, 113b may be caused in either direction along the furnace walls 108 and around the solid packing 105 to provide a good heat transfer convective heat transfer rate throughout the furnace 100. Both the fillers 104, 105 and the furnace walls 108. The penetration of the additional flames 112a, 112b into the furnace 100 is substantially improved as compared to mode 1 in which the flame 112 is utilized alone, and the overall deflation of the furnace 100 (from the burner 11 through the furnace headspace 106 to the flue) The air duct 110) is improved. Furthermore, by means of the reciprocating cycle between mode 2A and mode 2B, a high furnace temperature uniformity can be achieved.

Figures 9A through 9C and 15A through 15C show the results of a comparison of the temperature profiles (Figures 9A through 9C) of the prior art system operating continuously in mode 1 as in Figure 7 for system operation in mode 2A (Figures 15A through 15C). Comparing Fig. 9A with Fig. 15A shows that in mode 2A, a much higher flame temperature than mode 1 is achieved because mode 2a provides space for the flame to fully expand between the solid filler 105 and the furnace wall 108, rather than As mode 1 is a short cycle.

As a result, comparing FIG. 9B with FIG. 15B, the front side of the solid filler 105 is not in the mode 2A as compared with the mode 1 in which the front side of the solid filler 105 is excessively heated and the remaining portions of the fillers 104, 105 are colder. Excessively heated while significantly more heat reaches the back side of the solid filler and the molten filler 104 of the back side portion 118 of the furnace.

Similarly, comparing FIG. 9C with FIG. 15C, the furnace is in mode 2A compared to mode 1 in which only the front side portion 112 of the furnace wall 108 is warm and the back side portion 118 of the furnace wall 108 is cold. The wall temperature is relatively uniform throughout the furnace 100, with a slightly warmer point where the flame hits the wall 108.

Thus, solid packing heating and melting, filler temperature uniformity (and thus reduced packing loss due to overheating), and furnace wall temperature uniformity (and thus the packing is more uniform and faster) can be achieved by mode 2A or mode 2A operation. Great improvement in heating). Furthermore, by the cycle between mode 1 and mode 2A/2B, based on different sensing process parameters, the benefits of the two modes can be simultaneously achieved to optimize the melting and heating rate of the filler in the furnace. At the same time, product loss and refractory damage are reduced due to excessive heating.

In the third mode of operation (mode 3A) of FIG. 12, a pair of inclined side combustor members 20 are simultaneously active, and the central combustor member 20 It is passive, thereby creating two symmetric oblique flames 112a and 112b on either side of the furnace 100. This mode still allows each of the flames 112a, 112b to have sufficient space to fully deploy, and can use mode 2a or mode 2b alone or in succession to create a faster heating time.

In a variation of the second mode of operation (modes 2C and 2D) of Figures 13A and 13B, a burner as in Figures 5B(d), 5B(f) or 5C(c) is used, the central burner member 20 being blunt And two of the inclined burner members 20 of the symmetrical pair of side burner members 20 are active. As shown, the two inclined burner members 20 on the same side of the furnace are in motion, while the central burner member 20 and the two inclined burner members 20 on the other side of the furnace are passive. In mode 2C, this creates two differential tilting flames 112a and 112c on one side of the furnace 100, while in mode 2D, this creates two differential tilting flames 112b and 112d on opposite sides of the furnace 100. Note that in these modes, the central combustor member 20 can also cycle between active and passive states while maintaining the other combustor members 20 in the same state. As in mode 2A/2B, mode of operation 2C/2D enables the active flame to bypass the solid packing 105 at the center of the furnace 100 to bring the thermal energy to the back side portion 118 of the furnace 100. As shown in Figures 13A and 13B, the circulation of the products of combustion 113 can be caused in either direction along the walls of the furnace and around the solid filler to provide a good heat transfer convective heat transfer rate throughout the furnace 100 to the filler and Wait for the furnace wall. The penetration of the flame into the furnace is substantially improved compared to Mode 1, and the overall bleed of the furnace (from the burner through the furnace to the flue gas duct) is improved. Furthermore, by means of the reciprocating cycle between mode 2C and mode 2D, a high furnace temperature uniformity can be achieved. In addition, the inner and outer tilting burner members 20 are inclined downwardly at different angles, compared to the flames 112c and 112d. 112a and 112b can target the different areas of the unmelted filler and tilt a set of burners to encounter the packing closer to the front end 102 of the furnace 100 than the rest.

In a variation of the third mode of operation (mode 3B) of Figure 14, the two pairs of inclined side combustor members 20 are simultaneously active while the central combustor member 20 is passive. This mode still allows each flame to have sufficient space to fully deploy, and can use mode 2c or mode 2d alone or in combination to create a faster heating time. As shown, the flames 112a, 112b, 112c, and 112d are all active at the same time.

Figure 16 shows an end view of the burner 11 as viewed from the back side end 103 of the furnace 100 toward the packing door 102 as shown in Figure 5C(a) or Figure 5C(e), and showing the flames 120, 122a from each burner member 20. , 122b, 124 projection cross section. The burner 11 has a central burner member 20 that is oriented to produce a flame 120 of solid filler 105 that can strike the center of the furnace 100; a pair of symmetric inclined burner members 20 to which the central burner member is attached Either side 20 is for making flames 122a and 122b toward the area between the solid filler 105 and the furnace wall 108 in the center of the furnace 100; and an upper burner member 20 is provided to the central burner member 20 The upper position is suitably tilted to cause the flame 134 to face the top of the solid packing 105 of the furnace 100. The burner 11 can operate in any of the modes discussed above, and the combination of one, two or three combustor components 20 is active at any one time, and the other combustor components 20 are passive.

Figure 17 shows a three mode of operation of the burner 11 having a different burner angle 20 relative to the packing. One of the exemplary burners is shown in Figure 5C(d), wherein the upper burner member 20 is oriented to create a hold The flame 212a of the headspace above the packing 104, while the lower burner member 20 is oriented to create a flame 212b that slopes down against the packing 104, and specifically meets the possibility of focusing near the packing door 102. Any remaining solid filler 115. Other burner configurations including those of Figures 5B(a) through 5B(f) and 5C(a) through 5C(c) can also be constructed to operate in these modes. The burner 11 is operable in a three mode: the upper burner member 20 is in motion to create a pattern 4A of the flame 212a, the lower burner member 20 is in motion to create the flame 212b in mode 4B, and the upper and lower combustion The member 20 is active (and wherein the burner 11 has at least one other burner member 20 in a passive state) to simultaneously produce a pattern 4C of flames 212a and 212b. Mode A can be used to generally deliver energy to the furnace, and in particular to the molten bath, and Mode B can be used to carry additional energy to any solid debris placed in the appropriate position near the packing door, while Mode C is in combination with Mode A. And the characteristics of B.

The selective segmented burner 10 or the non-segmented burner 11 may comprise a combination of two or more burner members 20 that are co-located (in one or more outer casings) or located in the furnace The different positions of 100 (in two or more separate housings) and operate in a selective manner as described herein.

The controllers 190, 105 are constructed and programmed to enable selective active/passive ignition of individual burner components 20 in the combustor 11 to detect one or more process parameters in the furnace. The input and signal of the sensor are synchronized. Those process parameters may include, but are not limited to, and in any combination, fill gate temperature, flue gas temperature, flue gas composition or other flue gas properties such as optical properties, furnace back temperature (on the back side of the furnace), interior , embedded or external furnace wall temperature, time elapsed since the batch melting process, oxygen The change in the chemical and/or fuel supply pressure and any of the foregoing parameters over time.

Based on the process parameters, the controller 105 modifies or maintains one or more combustor members 20 in an active mode and modifies or maintains one or more combustor members 20 in a passive mode. More specifically, as discussed above, the proportional distribution reactant, the flow rate of the second fluid F2, remains constant in the annular nozzle 24 of each combustor member 20, and the selectively distributed reactant, the first fluid The flow rate of F1 will be adjusted to a higher active flow rate by a distribution nozzle 22, referred to as at least one burner member 20, and will be adjusted by a distribution nozzle 22 of at least one burner member 20, referred to as a passive state. Lower passivation flow rate. The controller repeats this mechanical action so that when the process transitions, the burner components 20 can be rapidly converted accordingly, so in some cases the previously passive state of the burner component 20 becomes active and the previously active combustion The member 20 becomes passive. However, it is noted that in certain process conditions, one or more of the combustor components 20 may remain in activity continuously and/or one or more of the combustor components 20 may remain in a passive state continuously.

In one embodiment of the combustor 10 or 11, the first fluid F1 is a fuel and the second fluid F2 is an oxidant. Preferably, the oxidant is at least 26% molecular oxygen, at least 40% molecular oxygen, at least 70% molecular oxygen, at least 98% molecular oxygen, or industrial pure oxygen. Thus, each of the combustor components 20 in the active mode operates in a fuel-rich manner (i.e., greater than one and up to an equivalent ratio of about 10), while each combustor component 20 in a passive mode operates in a fuel-poor manner ( That is, less than 1 and up to an equivalent ratio of about 0.2).

As discussed above, including a selective burner operating strategy for passing the burner through a plurality of different mode cycles based on a predetermined frequency, or The energy distribution demand decision of the furnace is determined manually (eg, by a furnace operator) or automatically by a sensor that is strategically required to be set according to the time required by the furnace.

The detection and control system is successfully implemented and the key to the benefits of the selective burner in the rotary furnace melting process.

Different detection methods and sensors can be used, as shown in FIG. 18 for example. Although several different sensors have been shown, any of them can be used by the controller 105 alone or in conjunction with other sensors to determine how to accentuate the operation of different burner components in time and space. The sensors may include one or more of the following: (a) one or more temperature sensors 150, such as thermocouples or non-contact or optical sensors (eg, UV and And/or an IR sensor), which can be used to detect an elevated temperature of the furnace front side portion 114 as a representation of solids in the furnace that impede flame deployment; (b) one or more temperature sensors 154, such as those established in the smoke A thermocouple or non-contact or optical sensor (eg, a UV and/or IR sensor) in the gas conduit 110 that can be used to detect the elevated temperature of the flue gas as a solid in the furnace that impedes flame deployment (c) one or more temperature sensors 160 located at appropriate locations outside the furnace for detecting elevated temperatures of the packing door 102 and/or the flue gas duct 110, and particularly non-contact or optical a sensor (152) one or more temperature sensors 152, 153 for detecting the temperature of different portions of the furnace, for example, embedded in or extending through the furnace wall 108 or the packing door 102 or the rear end a thermocouple or non-contact or optical sensor of wall 103 that is capable of detecting temperature gradients and inhomogeneities; (e) the flue gas A tube 110 or more in the nature of the exhaust gas sensor 155, which is an exhaust system for measuring properties such as composition represented by incomplete combustion; (f) in the flue gas duct One or more optical sensors 156 for detecting the optical properties of the flue gas; (g) one or more optical sensors 157 in the furnace wall 108 for detecting Measuring the optical properties of the furnace gas; (h) one or more proximal sensors 158 in the packing door 102 for detecting solid debris 105 in the furnace 100; (i) drum current a sensor (not shown) for detecting the motor current required to cause the furnace 100 to rotate about its axis, and a higher drum current indicating the presence of solids and a lower drum current indicating that the filler is completely melted; And (j) one or more pressure transducers 161 in the packing door 102 or the flue gas duct 110, and pressure fluctuations indicate greater combustion instability.

In one embodiment, one or more thermocouples may be provided on the furnace door alone or in combination with one or more radiation (IR/UV) sensors to detect the door and the outer sidewall or portion of the furnace or The temperature of one or more of the flue gas ducts (using a full view of the oven door). These temperature sensors are capable of detecting flame deflections that result in incomplete combustion, which may be caused by solid debris or packing in the furnace that prevents the flame from fully deploying. When the temperature of the door rises above a predetermined threshold and/or when the flame is detected by the radiation sensor, it can be interpreted as a short cycle of the flame in the furnace and can cause an obstruction. These effects include converting a flame toward one or more burner components of the solid debris from a passive state to activity while converting one or more burner components of the flame surrounding the solid debris from a passive state to an active state ( Or keep this burner component alive).

Alternatively, an optical (IR) pyrometer and/or imaging or image capture device may be placed in the oven door to detect solids in the furnace and prioritize (time weighting) to increase energy toward the solids. Heat transfer and faster melting. Correspondingly, one or more burners that direct the flame toward the solid debris The member can be converted from passive to active (or remain passive), while the flame can be converted from passive to active (or remain active) toward one or more burner components around the solid debris.

It can also be controlled according to the state of the melting cycle. At the top or initial portion of the melting cycle, when a flame oozes around the packing door or combustion occurs in the flue gas (the first or second hour, depending on the load and the overall cycle length), it is usually implied that One of them. First, the presence of oil or other flammable or volatile organic materials in the solid filler (fragment) results in sub-stoichiometric (fuel-rich) combustion because those organic materials burn off and consume the fuel supplied by the burner. Oxidizer. Second, the incomplete combustion caused by the limited penetration of the flame into the furnace causes a brief cycle of oxidant and fuel and combustion products because those gases deviate from the larger sized fragments of the furnace that have not yet melted. The tip of the melt cycle typically occurs during the first 1 to 2 hours of the melt cycle, depending on the load and overall cycle length.

The conditions associated with the tip of the melt cycle can be detected manually, or by means of different sensors, depending on the cycle time, or by operator observation. In the case of an organic component or a combustible material, U.S. Patent Application Serial No. 13/888,719, issued to U. . When the packing fragments are not oily or contain other organic or combustible materials, the detected flame and the resulting increase in temperature may be attributed to incomplete combustion and a brief cycle of flames that encounter large fragments located in the furnace. In this version, the combination of flames (one or more) may be operated simultaneously and/or in succession, as discussed above, to minimize the transient circulation of the flow and the (average) intensity flame around the door/flue gas duct to The smallest.

The scope of the present invention is not limited by the specific aspects or specific embodiments disclosed in the various embodiments, which are exemplified by any specific embodiments in which the aspects and functions of the invention are also within the scope of the invention. . Various modifications of the invention in addition to those shown and described herein will become apparent to those skilled in the art.

Α‧‧‧ burner member tilt angle

A‧‧‧ activity jet

P‧‧‧ Passive jet

10‧‧‧Selective burner

12‧‧‧Ontology

14‧‧‧Face

20‧‧‧ burner components

22‧‧‧Selective distribution nozzle

24‧‧‧Circular proportional distribution nozzle

30‧‧‧section nozzle

Claims (15)

A selective oxy-fuel burner for a packed door installed in a rotary kiln, the burner comprising: at least two burner members each igniting in different portions of the furnace, each burner member comprising: a selective distribution a nozzle configured to flow out of the first reactant; and a proportional distribution nozzle configured to flow out of the second reactant; at least one sensor for detecting one or more associated with furnace operation a multi-process parameter; and a controller programmed to independently control the flow of the first reactant to the respective selectively distributed nozzles based at least in part on the detected process parameters such that at least one of the combustor components is active At least one burner member is in a passive state, wherein a first reactant flow rate in the selectively distributed nozzle of the movable burner member is greater than an average first reactant flow rate to the selective distribution nozzles and the passive burner member The first reactant flow rate in the selectively distributed nozzle is less than the average first reactant flow rate to the selective distribution nozzles; wherein the second reactant system is substantially Proportionally distributed to the proportional distribution nozzles; and wherein the first reactant is one of a fuel and an oxidant and wherein the second reactant is the other of the fuel and the oxidant. A burner according to claim 1, wherein one of the at least two burner members has a flame axis substantially perpendicular to the packing door and the other of the at least two burner members has the packing door Vertical direction Zero angle, α, the axis of the flame; wherein the angle α is equal to or less than about 75°. The burner of claim 1, wherein the at least one sensor comprises an overheating sensor for detecting overheating of the stuffing door, wherein at least one active combustion is detected when excessive heating is detected The member is converted to a passive state while at least one of the burner components remains unchanged or converted to activity. The burner of claim 1, wherein the at least one sensor comprises an exhaust property sensor for detecting one or more changes in exhaust properties, wherein when the exhaust property indicates incomplete combustion At least one of the active burner components is converted to a passive state while at least one of the burner components remains unchanged or transitions from a passive state to an active state. The burner of claim 1, wherein the at least one sensor comprises an overheating sensor for detecting overheating of the stuffing door and an exhaust for detecting one or more changes in exhaust properties a property sensor in which overheating is detected and the venting property indicates incomplete combustion, at least one active burner component is converted to a passive state while at least one burner component remains unchanged or transitions from a passive state Be active. The burner of claim 1, wherein the at least one sensor comprises a non-contact sensor for detecting the presence of a solid filler that would impede flame deployment in the furnace, wherein the solid filler is present in In the furnace, at least one active burner component is converted to a passive state while at least one burner component remains Change or change from passive to active. A burner according to claim 1, wherein the proportional distribution nozzle is annular in the burner member and surrounds the selective distribution nozzle. The burner of claim 1, further comprising: at least one segmented nozzle spaced apart from each of the burner members and configured to constitute an outflow assisted second reactant; wherein the controller is further Programming is programmed to control the staging ratio to be less than or equal to about 75%, wherein the segment ratio is the ratio of the second reactant contained in the auxiliary second reactant flow to the total flow of the second reactant . A rotary furnace comprising: a packing door and an exhaust port disposed at one end of the furnace; and an oxy-fuel burner mounted to the packing door, the burner comprising: at least two burners Components each igniting into different portions of the furnace, each burner member comprising: a selectively distributed nozzle configured to flow out of the first reactant; and a proportional distribution nozzle configured to flow out of the oxide At least one sensor for detecting one or more process parameters in the furnace; and a controller programmed to be at least partially based on the detected system The process parameters independently control the flow of the first reactants to the respective selectively distributed nozzles such that at least one of the combustor components is active and at least one of the combustor components is passive, wherein the selectively distributed nozzles of the movable combustor components The first reactant flow rate is greater than the average first reactant flow rate to the selective distribution nozzles and the first reactant flow rate in the selective distribution nozzle of the passive burner member is less than the delivery to the selective distribution nozzles An average first reactant flow rate; wherein the second reactant is substantially proportionally distributed to the proportional distribution nozzle; and wherein the first reactant is one of a fuel and an oxidant and wherein the second reactant system The other of the fuel and oxidizer. A method of operating a rotary kiln having a packing door and an exhaust port disposed at one end of the furnace and an oxy-fuel burner mounted to the packing door, the burner having respective ignitions in different portions of the furnace At least two burner members, each burner member comprising a selectively distributed nozzle and a proportional distribution nozzle, the burner additionally having a programmed program to independently control the first reactant flow rate of the selectively distributed nozzles delivered to each of the burner members The second reactant flow rate to the proportional distribution nozzles is substantially proportionally distributed, the method comprising: detecting one or more process parameters in the furnace; at least in part based on the selected process parameter selection At least one of the burner members is active and at least one of the burner members is passive; flowing the first reactant through the at least one movable burner at a reactive injection flow rate a selectively distributing nozzle of the member; flowing the first reactant through the selective distribution nozzle of the at least one passive burner member at a passive injection flow rate; and flowing the second reactant substantially proportionally through the proportional distribution nozzles Wherein the active injection flow rate is greater than the average flow rate through the selectively distributed nozzles and the passive flow rate is less than the average flow rate through the selectively distributed nozzles; and one of the first reactant fuels and oxidants And wherein the second reactant is the other of the fuel and the oxidant. The method of claim 10, further comprising: detecting excessive heating of the stuffing door; and detecting excessive heating, converting at least one active burner member into a passive state while at least A further burner component remains active or converted to activity. The method of claim 10, further comprising: detecting at least one exhaust property; converting the at least one active combustor member into a passive state when the exhaust property indicates incomplete combustion, while at least A further burner component remains active or converted to activity. The method of claim 10, further comprising: detecting when the at least one active burner component is launched into the furnace a flame of the solid filler; and converting the at least one active burner member into a passive state while maintaining at least one other burner member active or converted to activity. The method of claim 10, wherein the ratio of the active injection flow rate to the passive injection flow rate is from about 5 to about 40. The method of claim 10, wherein the passive burner member has an equivalence ratio of from about 0.2 to about 1, and wherein the movable burner member has an equivalence ratio of from about 1 to about 10, wherein the equivalence ratio is theoretical stoichiometry The ratio of oxidant flow to the actual oxidant flow through the distributed nozzles to combust the fuel flowing through the remaining distributed nozzles.